Single action can openers



March 31, 1959 R. E. MGLEAN 2,879,590

SINGLE ACTION CAN OPENERS Filed Oct. 4, 1956 5 Sheets-Sheet 1 INVENTOR. PO/V E. McL em;

ATTOKNEK R. E. MLEAN SINGLE ACTION CA-N OPENERS March 31, 1959 3 Sheets-Sheet 2 Filed 'Oct. 4, 1956 RM 0 6 WM Jim 6 W ATTORNEK March 31, 1959 Filed Oct. 4, 1956 R. E. M LEAN SINGLE ACTION CAN OPENERS i l l 3 Sheets-Sheet 3 INVENTOR. Faefif .E M0124 ,4 TTORNEK United States Patent 2,879,590 SINGLE ACTION CAN OPENERS Robert E. McLean, Kansas City, Mo., assignor to John C. Hockery, Kansas City, Kans., as trustee Application October 4, 1956, Serial No. 613,895 9 Claims. (Cl. 30-155) This invention relates to can openers and refers more particularly to a single action can opener of the type wherein all of the operative steps required for permitting insertion of a can rim, puncturing of the can lid, subsequent cutting of the lid from the can, and release of the can from the device, are performed by manipulation and rotation of a single operating handle.

This application is a continuation-in-part of my copending application Serial No. 591,899, filed June 18, 1956, now Patent No. 2,814,103, issued November 26, 1957.

In my co-pending application referred to above, there is disclosed a single action can opener of the type in which all of the essential steps of opening a can are accomplished by rotation in selected directions of a single operating handle. The present invention has for one of its primary objects the provision of an improved can opener of this type in which the operating mechanism is considerably simplified and which is better suited for heavy duty use.

A further object of the present invention is to provide a single action can opener of the character. described in which means are provided for releasably stabilizing the feed wheel of the can opener in a cocked position in which the feed wheel is separated from the cutter wheel a distance sufficient to permit insertion therebetween of a can flange or rim. In the construction disclosed in my co-pending application the operator is required to maintain a continuous force on the operating handle to maintain the feed wheel in the separated relationship from the cutter wheel. The cocking feature embodied in the present invention thus represents one of the im provements over the disclosure of the co-pending application.

Still another object of the invention is to provide a can opener of the character described in which means are provided for positively insuring return of the feed wheel to can shearing relationship with the cutter wheel following puncturing of the can as the shearing operation is initiated.

Still another object of the invention is to provide a can opener of the character described in which the bulk of the moving parts of the operating mechanism are located within a casing or housing, thus providing greater safety in operation and little likelihood of mechanical damage under rough treatment.

A further object of the invention is to provide operating mechanism for single action can openers which is readily adaptable to either a hand held unit or a wall mounted unit.

Other and further objects of the invention, together with the features of novelty appurtenant thereto will appear in the course of the following description.

In the accompanying drawings, which form a part of the specification and are to be read in conjunction therewith, and in which like reference numerals indicate like parts in the various views:

Fig. 1 is a side elevation of a preferred unit embodying 2,879,590 Patented Mar. 31, 1959 2 the invention, the handle and associated parts being shown in full and broken lines to illustrate ditferent phases of operation;

Fig. 2 is a side elevation taken from the opposite side of the unit illustrated in Fig. 1;

Fig. 3 is a top plan view of the preferred unit, parts being broken away for purposes of illustration;

Fig. 4 is an enlarged fragmentary view similar to Fig. 1, but with the handle and hub removed and with other parts broken away for purposes of illustration;

Fig. 5 is an end view taken from the right hand end of Fig. 1;

Fig. 6 is a sectional view taken along the line 6-6 of Fig. 4 in the direction of the arrows, and showing the handle assembly in place on the unit but at a different point of rotation from that illustrated in Figs. 1 and 2;

Fig. 7 is an exploded perspective view of the preferred unit, the spring and plunger not being shown;

Fig. 8 is a perspective view of a portion of a unit in which is employed a modified camming and fulcrum arrangement, the handle assembly not being shown; and

Fig. 9 is a side elevation from the handle side of a wall mounted unit, the handle being removed and the modified camming and fulcrum arrangement represented by Fig. 8 being employed.

Referring to the drawings and initially to Figs. l-7, inclusive, the preferred unit comprises a can opener intended to be held, while being used, in the hand of an operator rather than mounted on a wall or support. Reference numeral 10 indicates the main body of the unit, this comprising a machined or cast piece having a hand grip portion 10a and at one end an enlarged head portion 10b. One side of the head portion is formed as a flat face on which, as will later be described in more detail, is mounted a can cutter wheel 11 along with can guide members. The lower edge of the face 100 is preferably of a smooth arcuate configuration. A serrated feed wheel 12 is provided adjacent the cutting wheel and this feed wheel is mounted on a shaft 13 having secured to its other end an operating handle assembly 14. Through mechanism later to be described, all necessary operations of the can opener are obtained through manipulation of the handle assembly 14 alone.

As is best seen in Figs. 2 and 6, the cutter wheel 11 for the unit is of the conventional rotatable grooved type. It is fixed to the body of a unit on an inclined axis by means of a screw cap spindle 15 which has a reduced diameter threaded extension 15a. The extension 15a is threaded into a tapped hole formed in the can opener body. A boss having an inclined face is formed on the body and a washer 16 is provided to properly locate the spindle and cutter wheel with respect thereto. The feed wheel 12 is positioned below the cutter wheel with its serrated periphery extending into the groove in the cutter wheel (see Fig. 6). Positioned below the feed wheel on face 100 is a projecting circular boss 17 which, when the unit is in use, engages the side of a can to hold it in desired vertical position. This boss is preferably provided with acentral bore in which are received outwardly sprung prongs 18 on a cap piece 19 which serves as the bearing surface for the can wall. Tilting of the can during the cutting operation is resisted by a projecting guide pin 20 secured to face 100 and located to one side of and on a level with the intersection of the feed wheel with the cutter wheel. The length of the guide pin 20 is such that it will overlie and bear down on the rim of the can when the latter is engaged between the cutter and feed wheels during the cutting operation later to be described. A second guide member 20a is provided to prevent the can from swinging inwardly toward face 10c during the cutting operation.

The opposite side of the head from face 10 is formed by a flat plate member 21 which is disposed parallel to face c and which provides the opposite side face for the head portion of the unit. As is shown best in Fig. 7, the plate member 21 has a rather narrow extension 21a which is secured to body 10 by a screw 22. The extension 21a and an adjacent portion of the plate are seated in a shallow recess 23 of thesame configuration so that the plate is generally flush with the side of the body.

At the head end of the body material is cut away from the body to provide a recess of somewhat irregular shape having for one side the inside surface of plate 21 and for the opposite sidethe inside surface 10d of face 10c. Contained within this recess and of only slightly less thickness than the space between surface 10d and the plate 21 is a feed wheel carrier member 24 which is formed to operate as a bell crank. The carrier member 24 is pivoted between the surface 10d and plate member 21 on an axis normal thereto by a pin 25. As is shown in Fig. 7, the carrier member or hell crank 24 has a relatively large base leg 24a and a narrower upstanding leg 24b. The outer edge 240 of the bell crank is shapedto conform with the curvature of the corresponding edges of plate 21 and plate 100 so that these edges in the normal position of the bell crank are flush with one another. Referring again to Figs. 4 and 7, the base leg 24a of the carrier member or hell crank 24 is formed to provide a convex upper edge 24d. An arcuate flange or raised rib Me is formed on this edge, the flange being located on that side of the bell crank adjacent plate 21 and its one side face forming an extension of the side face of the bell crank. The purpose of this flange will be later described.

The inner edge 26 of the bell crank recess is curved quite similarly to the configuration of the inner edge of the bell crank; however, that portion 27 of the edge of the recess which rises with the upright leg 24b of the bell crank is cut back at an angle sufficient to permit rocking movement of the bell crank counter-clockwise (as viewed in Fig. 4) about its pin 25. It will also be noted that a depression having base 28 is provided along the edge 26 of the bell crank recess to accommodate the flange Me on the bell crank and to permit the rocking movement described without interference from the flange.

In the normal position of the bell crank 24, which is shown in Figs. 4 and 6, the upper edge 24d of the bell crank abuts tightly against the edge 26 of the bell crank recess, thus preventing further movement of the bell crank in a clockwise direction. This position of the bell crank is yieldably maintained by means of a spring loaded plunger 29 having a nose which seats in a socket 30 (see Fig. 7) formed on the inside of the upstanding leg 24b. The plunger 29 is oriented generally longitudinally of body 10 and is contained within an open face cavity 31 formed in body 10 and covered by plate 21. That end of plunger 29 opposite the nose is provided with a reduced diameter portion 29a which is received within a guide and centering sleeve 32, carried in a cavity 33 aligned with cavity 31 and of somewhat greater cross sectional area. The end of said sleeve adjacent the plunger is provided with a radial flange 32a which slidably fits within the cavity 33. A coiled compression spring 34 provides the force urging the plunger longitudinally toward the bell crank, this spring encircling the sleeve and abutting at one end against the end wall 35 of cavity 33, and at the other against flange 32a.

The feed wheel 12, shaft 13 and handle assembly 14 of the unit are carried by the base leg 24a of bell crank 24. As best seen in Fig. 6, the bell crank is provided with a circular aperture 36 of somewhat greater diameter than shaft 13 and through which the shaft extends to opposite sides of the body. The shaft is journaled in this aperture by means of a pair of opposed radially flanged bushings 37 which are press-fitted into the opposite ends of the aperture and which serve to rotatably support shaft 13 therein. At one end the shaft is provided with a reduced diameter threaded portion 13a on which is threaded the feedwheel 12. Between the feed wheel and the end face of the adjacent bushing 37 are located spacing shims 39 and a thrust washer 39a of thickness necessary to provide the desired axial location of feed wheel 12 relative the cutter wheel 11. An aperture 10 is provided in face 1000f the body to permit insertion of shaft 13 therethrough. This aperture 15 generally oblong in shape and is of sufliciently greater length and width than the diameter of the, flange of bushing 37 to permit the movement of the shaft and bell crank later to be described.

The handle assembly 14 is secured to that end of shaft 13 opposite from the feed wheel 12. Preferably the handle assembly includes a hollow circular hub portion 14a provided with an internal central plug 40 from which radiate strengthening webs 41 and 42. The web 42 is of somewhat greater thickness than the other two for a purpose later to be described. The hub is secured to shaft 13 by means of a threaded connection, the shaft being provided with a threaded reduced diameter portion 13b which is threaded into a tapped central aperture in the plug 40. A washer 43 is recessed in the plug and an annular shim 44 surrounds the shaft adjacent the washer 43. It will be noted that the main body of shaft 13 is of such length that it extends at the right hand end (as viewed in Fig. 6) slightly beyond the outer face of the adjacent bushing 37. In the space provided between the face of this bushing and the shim 44 there is located a resilient and yieldable annular spring washer 45 which serves to exert a continuous yieldable axial force on the handle to maintain the feed wheel 12 in such lateral plane that it cannot clash with the cutting edge of the overlying cutter wheel. This spring tension also prevents the handle from turning unless-manually operated. Spaced radially from the axis of shaft 13 and carried by the web 42 of the handle assembly is the camming and fulcrum pawl 46 of the unit. In its preferred form pawl 46 comprises a cylindrical pin positioned parallel with the axis of shaft 13. The pin is slidably received within a corresponding cylindrical cavity 47 formed in web 42. The inner end of the pin is provided with a central bore in which is positioned a helical compression spring 48 which extends from the bore and seats at its other end against the base of the pin cavity 47. As will be evident, spring 48 serves to yieldably urge the pin at all times inwardly toward the can opener body. The pin or pawl 46 and its carrying web 42 are preferably located at approximately with respect to the longitudinal axis of the handle assembly, but may be located at any other desired position.

Returning now to Figs. 4 and 7,-it will be observed that provided in the plate member 21 is an enlarged uniquely configurated aperture which surorunds the shaft 13. Above the shaft 13 the edge of this aperture (which is at all points normal to the plate 21 and the side surface of bell crank 24) forms an essentially horizontal portion 49 which will hereinafter be referred to as the fulcrum surface. The horizontal portion 49 or fulcrum surface extends completely over the center of shaft 13 and terminates at its left hand end (as viewed in Fig. 4) in a downwardly arcuate stop portion 50. At the right hand end the fulcrum surface 49 merges with a curved portion 51 which in turn leads into a portion 52 which swings in an are below the shaft 13 to the opposite side thereof. The portion 52 can conveniently be described as being divided into three sections, the first of which extends from a to b, the second from b to c, and the third from c to d (see Fig. 4). That section from a to b is so spaced from the center of shaft 13 as to lie outside the orbital path of the handle pawl 46 at all times during the operation of the can opener, even at, times when the shaft is displaced downwardly from its normal position due to pivoting of the bell crank as later to be described. The'section of arc'52 from 'b to c is formed so that at of the bell crank to the plane of the outer face all times when the feed wheel shaft 13 is displaced downwardly from the normal position it will lie within the orbital path of the handle pawl 46 and engage same. However, when the shaft is in the normal position (including can engaged position), section bc, like section a-b, lies entirely outside the orbital path of the handle pawl. The section to d is shaped to lie outside the orbital path of the pawl at all times during rotation of the handle. At the end of this section is provided an inclined ramp 53 which preferably is formed as an ear struck from the metal of the plate member 21 and bent inwardly toward the body of the can opener. A recess 54 (see Fig. 7) is provided in the can opener body to accommodate this ramp. As will be evident, ramp 53 provides a smooth inclined surface lying in the path of handle pawl 46 and leading from the plane of the side face of plate member 21.

In the operation of the unit disclosed in Figs. 1-7, inclusive, the first step to be taken when it is desired to open a can is to rotate the handle assembly 14, starting from any position of the handle assembly, counterclockwise (as viewed in Fig. 1) until the pawl 46 on the handle assembly engages with the arcuate portion 51 at the end of the fulcrum surface 49. The position of the handle assembly at the point of such engagement is illustrated in solid lines in Figs. 1 and 2 and the corresponding position of pawl 46 is shown in broken lines in 'Fig. 4. During this preliminary rotaton of the handle, the bell crank member 24 remains in the normal position due to the influence of spring 34 previously described. In this position it will be noted that feed wheel 12 has its upper margin positioned in the annular groove of the cutter wheel 11. To separate the two wheels in order to permit insertion of a can flange between them preparatory to opening the can it is necessary to lower the feed wheel and this is accomplished by further rotation of the handle assembly counter-clockwise from the position illustrated in solid lines in Fig. I.

At the beginning of such rotation and as earlier mentioned, the pawl 46 occupies the position shown in broken lines in Fig. 4. In this position the free end of the pawl slidably rests against the adjacent side face of bell crank 24 and the periphery of the pawl bears radially against the surface 51. As a continuing counter-clockwise rotative force is applied to the handle, the fulcrum reaction between the pawl and surface 51 causes the handle to pivot about the point of contact between the pawl and fulcrum surface, thus depressing the shaft 13 and causing bell crank 24 to rock counter-clockwise about its pivot pin 25 against the pressure of spring 34. As will be evident, the movement of the handle with the pawl serving as the fulcrum causes the feed wheel and shaft 13 to move downwardly as a unit and opens the space between the feed wheel and cutter wheel for insertion of a can flange.

Now it will be evident that as the shaft 13 and feed wheel are displaced downwardly, the pawl 46 will slide across the fulcrum surface 49 while maintaining continuous fulcrum contact therewith. As the bell crank moves downwardly, continuous end supportfor the pawl is provided by the flange 24a formed on the bell crank. During the initial portion of this sliding movement, the spring 34, acting through the bell crank, provides a clockwise turning moment actingon the handle which must be overcome by the hand force applied by the operator. However, the pawl soon reaches a point on the fulcrum surface where the reaction force between the pawl and fulcrum surface is on a line with the center of shaft 13. In the illustrated embodiment this position, which is the dead center position, is reached when the center of the pawl is exactly vertically above shaft 13. Further movement of the pawl to the left of this dead center position creates a condition in which the rotative force applied to the handle by the spring and bell crank counter-,

clockwise instead of clockwise. Once the pawl has passed the dead center position, it is engaged by the curved seat or stop 50 and further movement to the left (and thus further counterclockwise movement of the handle) is prevented. The position of the handle when this occurs is illustrated in broken lines in Figs. 1 and 2, and the corresponding position of the bell crank and feed wheel is likewise shown in broken lines. Due to the interaction of the forces supplied by fulcrum surface 49 and stop 50 on the pawl 46 and the continuous yieldable force supplied by spring 34, the handle-feed wheel assembly and bell crank will remain stabilized in the broken line position illustrated in Figs. 1 and 2 when the handle .is released by the operator. The broken line position can thus best be described as a cocked position in which the unit is ready for insertion of a can flange between the cutter wheel and feed wheel. 7

While the operating mechanism is in the cocked position just described, the can opener unit can now be positioned so that the cutter wheel 11 rests on a can just inside the flange with the feed wheel 12 spaced below the flange. The operator then applies a clockwise rotation to the handle suflicient to overcome the moment created by spring 34 and to move the pawl 46 to the right on fulcrum surface 49 back through the dead center position. Once through the dead center position, the spring 34 will aid in rocking bell crank 24 in a clockwise direction to bring the feed wheel 12 upwardly into firm engagement with the underside of the can flange or bead.

In the preferred unit the pressure of spring 34 is such that it supplies slightly less force than that required to cause the puncturing or piercing of the can top by the cutter wheel following engagement of the feed wheel with the can rim. The spring must be strong enough, however, to firmly wedge the can rim between the cutter and feed wheels so that the rim will be held therein. For conventional food cans for domestic use, I have found that the spring 34 should be given a strength such that the feed wheel is urged upwardly toward the cutter wheel by a force of approximately 50 pounds. This force is nearly adequate, but not quite so, for piercing the end of a can.

Since the force of the spring is not quite enough to cause piercing of the can lid by the. cutter wheel 11 it will be understood that the feed wheel is not yet returned to the normal position illustrated in Figs. 2, 4, and 6, but remains spaced below the cutter wheel. However, a the operator continues the clockwise rotation of the handle, the periphery of pawl 46 engages the curved section b--c of the are 52 of the aperture in plate member 21. As has earlier been noted, this section of are 52 is located so as to lie within the orbital path of the pawl at all times except when the feed wheel and bell crank are in the normal up position. During this movement, the end of the pawl 46 remains in sliding contact with the face of the bell crank and free from contact with sections a b of the are 52, since as earlier noted, section ab is so located as to be at all times outside the orbital path of the pawl. However, once pawl 46 is intercepted by section b-c, continued rotation of the handle in the clockwise direction forces the pawl to follow the path defined by section b-c, thus creating a positive upward force on the handle-feed wheel assembly and bell crank which is suflicient to force the can upwardly with respect to the cutter wheel and cause puncturing of the can by the cutter wheel. However, it should be noted that this positive upward force is materially supplemented by the force of spring 34, and this greatly facilitates the piercing of the end of the can by the cutter wheel. The section b-c of are 52 thus serves as a camming surface which cooperates with pawl 46 to complete the puncturing of the can. After puncturing of the can the feed wheel is located in its up or normal position and rotation of the handle can be continued to drive the can flange in the usual fashion.

The feed wheel is held in the up position by the action of spring 34. However, when the rim or flange of any can is so engaged in the device, the portion 24d of the bell crank 24 cannot seat upwardly against portion 26 of the body 10.

Force of spring 34 is adequate to always vertically squeeze the rim or flange of a can between the feed wheel and overlying grooved portion of the cutter wheel, after the end of any can has been pierced by the cutter wheel. Also, after piercing, the feed wheel is maintained upwardly by the spring 34 at such height that the periphery of pawl 46 clears the camming surface bc of the are 52. The position of the feed wheel 12 and bell crank 24 is substantially the same when the can flange is engaged between the feed wheel and cutter wheel as the normal position for these parts shown in Figs. 2 and 6. However, due to the thickness of the can flange, and as has been noted earlier, the feed wheel does not return fully to the normal position, but may be a few thousandths of an inch below. It will be understood that in referring to the normal position in the specification and claims, this language also includes the normal cancutting position.

It will be noted that as rotation is continued, the pawl 46 is lifted from the face of the bell crank to the level of the face of plate 21 by means of the inclined surface or ramp 53 and that during approximately 150 of rotation the pawl rides on the face of plate 21. So long as clockwise rotation of the handle continues, and through any number of revolutions, pawl 46 remains inoperative except to move inwardly to ride on the bell crank 24 after the pawl moves past the fulcrum surface 49 and its extension 51, and to be forced outwardly again when it reaches ramp 53.

By simply reversing the direction of handle rotation when the cutting operation is completed, and again bringing pawl 46 into engagement with the fulcrum surface 49 and following the procedure earlier outlined for coupling the can opener with the can, the feed wheel can be separated from the cutter wheel to permit removal of the can flange from the can opener.

Since the feed wheel 12 is held in its up position through the medium of spring 34, it will be evident that the unit is admirably adaptable to the passing through the cutting area of the side seam of a can. Smooth passage of this seam depends on permitting a slight degree of vertical separation between the feed wheel and cutter wheel. The slight vertical separation necessary for passage of the can seam is easily obtained through the mobility of the feed wheel relative the cutter wheel and the constant upward, but yieldable, pressure exerted by spring 34.

In Fig. 8 there is shown a modified can opener which is identical in all respects to the can opener previously described with the exception that the fulcrum surface is so arranged as to not provide for the cocking action present in the previous embodiment. In the modified unit there is provided the body 110, plate member 121, bell crank 124, and feed wheel shaft 113, along with every other feature of the embodiment described in connection with Figs. 1-7, inclusive. While not shown in Fig. 8 the handle assembly is likewise identical to that previously described, being connected with the feed wheel shaft 113. The only difference between the modified unit of Fig. 8 and that previously described is that the fulcrum surface 149 is positioned on a level with the feed wheel shaft and thus the pawl on the handle assembly is not capable of moving over center with respect to the shaft when the handle is employed as a lever to depress the feed wheel. In the modified unit, the operator must maintain a continuous counter-clockwise force on the handle in order to maintain the feed wheel vertically separated from the cutter wheel, all as disclosed in my aforesaid .co-pending application Serial No. 591,899.

In Fig. 9 there is shown a unit which is adapted for wall mounting and which employs a fulcrum surface identical in operation to that shown in Fig. 8. Here the can opener body 210 is provided with a flared base 210 which is adapted to be mounted on a wall or similar vertical surface by means of a bracket (not shown). It will be understood that the body 210 projects horizontally outward or forward from the supporting surface. Any conventional mounting bracket and associated connection for the can opener may be used.

The fundamental diiference between the unit shown in Fig. 9, on the one hand, and that disclosed in Figs. 1-7, inclusive, on the other (other than the location of fulcrum surface mentioned above) is that all operating parts are reversed so as to put the handle in the wall mounted unit on the opposite side from its location in the hand held unit. The only additional structural change required is that the bell crank 224 be provided with a recess 254 to accommodate the pawl ramp 253 bent inwardly from plate 221. This recess must be given dimensions such that rocking movement of the bell crank can be accomplished without interference so that when the bell crank 224 is in the up or normal position (illustrated in Fig. 9) the space between the lower edge 254a of recess 254 and the end of the ramp will be small enough to permit smooth transition of the pawl end from the face of the bell crank to the ramp 253 during rotation of the handle. While the handle assembly is not shown it is identical to that shown and described earlier herein except for rotational repositioning of the pawl 46 to any preferred location or timing, and is connected with the feed wheel shaft 213 ponrnaled in the bell crank 224. The feed wheel, cutter wheel and can guides are, as in earlier embodiments, located on the opposite side of the unit from that shown in Fig. 9, and their arrangement and manner of operation are the same as earlier set forth.

From the foregoing it will be seen that this invention is one well adapted to attain all of the ends and objects hereinabove set forth together with other advantages which are obvious and which are inherent to the structure.

It will be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of the claims.

As many possible embodiments may be made of the invention without departing from the scope thereof, it is to be understood that all matter herein set forth or shown in the accompanying drawings is to be interpreted as illustrative and not in a limiting sense.

Having thus described my invention, I claim:

1. In a single action can opener, a stationary body, a cutter wheel and cooperating feed wheel, one of said wheels mounted on said body to rotate about a fixed axis, a movable member pivotally connected with said body, the other of said wheels being mounted on said movable member, the pivot axis of said movable member being so located that rocking of said member on its pivot changes the vertical spacing between the wheels, said member having a first position in which said wheels are substantially in can cutting relationship and a second position in which they are vertically separated from one another sufiiciently to permit insertion and removal of a can flange therebetween, a rotary crank member carried by said movable member and coupled with said other wheel for turning same, cooperating means on said crank member and body operative to rock said movable member on its pivot to said second position on rotation of said crank in one direction, said last mentioned means including mechanism operable upon further rotation of said crank in said one direction after the movable member has reached its second position to releasably stabilize said carrier member in a cooked second position. v

2. A single action can opener comprising a can opener body, a cutter wheel rotatably fixed to one side of said body, a feed wheel normally disposed in operative can cutting relationship with said cutter wheel, a feed wheel carrier member, said feed wheel supported on said carrier member, means mounting said carrier member on said body for movement relative said body in a direction to vertically separate said feed wheel from said cutter wheel, yieldable resilient means continually urging said carrier member into the normal position for said feed wheel, a drive shaft for said feed wheel rotatably supported by said carrier member, cooperating pawl and fulcrum means connected respectively with said shaft and body, and operable upon rotation of said shaft in one direction to cause said carrier to move in a direction to vertically separate said feed wheel from said cutter wheel, said fulcrum means having a portion cooperating with said pawl means upon further rotation of said shaft in said one direction after the feed wheel is separated from the cutter wheet to releasably stabilize said carrier member in a cocked position in which said feed wheel is separated from said cutter wheel a distance sufficient to receive therebetween a can flange.

3. A single action can opener comprising a can opener position to which said movable member remains in its body, a cutter wheel rotatably mounted in a fixed position on one side of said body, an elongate aperture through said body having one end closely adjacent said cutter wheel, a rotatable shaft extending through said aperture, a feed wheel mounted on that end of said shaft on the same side of said body as said cutter wheel, a handle assembly mounted on the other end of said shaft and on the opposite side of said body from the cutter and feed wheels, said feed wheel, shaft and handle assembly forming together a unitary-feed wheel assembly movable in said slot toward and away from said cutter wheel, yieldable resilient means associated with said handle-feed wheel assembly normally urging said handlefeed wheel assembly toward the end of said aperture nearest the cutter wheel, a pawl spaced radially from said shaft and connected with said shaft for rotation therewith, an abutment carried by said body and dis posed in the path of said pawl and adapted to engage same once said shaft is rotated in one direction, said abutment operable upon further rotation of said shaft in said direction after engagemnet of said pawl with said abutment to cause said handle-feed wheel assembly to be displaced against the influence of said yieldable resilient means in a direction to vertically separate said feed wheel from said cutter wheel, said abutment being so constructed and arranged as to cause said pawl to move through a dead center position on the other side of which the tendency of the yieldable resilient means acting on the handlefeed wheel assembly is to apply a rotative force on said shaft tending to continue the movement of said shaft in said one direction, and stop means positioned for engagement by said pawl following movement thereof through said dead center position, thereby to stabilize said handle-feed wheel assembly in a cocked position in which said feed wheel is vertically separated from said cutter wheel a distance sufficient to receive therebetween a can flange.

4. A single action can opener comprising a can opener body having at one end a pair of spaced parallel plate members defining a space therebetween, a bell crank member disposed in said space and pivoted between said plates for rocking movement about an axis normal to said plates, a cutter wheel rotatably mounted in a fixed position on the exterior of one of said plates, a shaft extending through enlarged apertures provided in the respective plates and rotatably journaled in one leg of said bell crank, a feed wheel secured to that end of said shaft on the same side of said body as said cutter wheel, a handle assembly connected with the other end of said shaft on the opposite side of said body for rotating said shaft and feed wheel, yieldable resilient means contained within said bodycontinually urging said bell crank in a direction to urge said feed wheel vertically toward said cutter wheel, stop means on said body arranged for enment by saidbell crank to stop it at a normal position wherein said feed wheel is substantially in operative can cutting relationship with said cutter wheel, a fulcrum surface carried by that plate member adjacent the handle assembly, and means carried by the handle assembly adapted to engage said fulcrum surface upon rotation of said handle-feed wheel assembly in one direction and operable to rock said bell crank in a direction to move said feed wheel vertically away from said cutter wheel a distance sufficient to permit insertion between said wheels of a can flange.

S. A single action can opener as in claim 4 including a camming surface arranged to cooperate with said last mentioned means when said handle-feed wheel assembly is rotated in the other direction and operable to exert a positive force on said handle-feed wheel assembly to return said bell crank to said normal position upon failure of said bell crank to reach said position under the influence of said yieldable resilient means alone.

6. A single action can opener as in claim 4 wherein said yieldable resilient means comprises a reciprocable plunger contained within a cavity in said body and arranged to abut at one end the other leg of said bell crank, and a compression spring surrounding said plunger and continually urging same toward said other leg.

7. A single action can opener comprising a can opener body having at one end a pair of spaced parallel plate members defining a space therebetween, a bell crank member disposed in said space and pivoted between said plates for rocking movement about an axis normal to said plates, a cutter wheel rotatably mounted in a fixed position on the exterior of one of said plates, a shaft extending through enlarged apertures provided in the respective plates and rotatably journaled in one leg of said bell crank, a feed wheel secured to that end of said shaft on the same side of said body as said cutter wheel, a handle assembly connected with the other end of said shaft on the opposite side of said body for rotating said shaft and feed wheel, yieldable resilient means contained within said body continually urging said bell crank in a direction to urge said feed wheel vertically toward said cutter wheel, stop means on said body arranged for engagement by said bell crank to stop it at a normal position wherein said feed wheel is substantially in operative can cutting relationship with said cutter wheel, a pawl carried by said handle assembly and spaced radially from the shaft axis, said pawl extending inwardly toward said bell crank and movable in a direction parallel to the shaft axis, means yieldably urging said pawl toward said bell crank, the aperture in that plate adjacent said handle assembly being formed with a portion of its edge defining a fulcrum surface extending in a direction transverse to the normal rotary path of said pawl whereby upon rotation of said handle assembly in one direction said pawl will engage said fulcrum surface, and, upon further rotation of said handle in the same direction, to cause said handle assembly to act as a lever which rocks said bell crank in a direction to vertically separate said feed wheel from said cutter wheel, the plate being provided with lift means for lifting said pawl out of said aperture during rotation of said crank in the opposite direction whereby smooth continuous rotation of said handle in said opposite direction is permitted when said bell crank is in said normal position.

8. A single action can opener as in claim 7 wherein said fulcrum surface is of a length such and so oriented that upon engagement of said pawl with said surface and further rocking of said bell crank beyond the point necessary to vertically separate said feed wheel from said cutter wheel said pawl travels along said fulcrum surface between said fulcrum surface and said shaft past dead center, and including stop means for limiting the travel of said pawl after its movement through dead center thereby to stabilize the bell crank in a cocked position in' which the feed wheel is vertically separated from the cutter wheel a distance sufiicient to permit insertion of a can bead therebetween.

9. A single action can opener as in claim 7 wherein another portion of the edge of said aperture is formed for engagement by said pawl at a point to positively 12 force said bell crank toward its normal position when said handle is rotated in the other direction and said bell crank fails to return to said normal position under the influence of said yieldable resilient means alone.

References Cited in the file of this patent UNITED STATES PATENTS 2,532,121 Rush Nov. 28, 1950 10 2,565,048 Rush Aug. 21, 1951 2,651,838 Curtis Sept. 15, 1953 

